Controlling vibrations

ABSTRACT

In order to control vibrations of two parts of a piece of machinery, a variable force may be generated to oppose the vibrations, with the variable force being generated under control of a controller on the basis of an iterative relationship, the iterative relationship being such as to generate the force of one iteration using a controller output signal in frequency domain vector form derived from the controller output signal of the immediately previous iteration in frequency domain vector form plus a frequency domain vector quantity derived from the resultant vibration of more than one previous iteration. 
     Where these two parts are connected by multiple (f) mounting devices, the controller output signals a previous iterations are taken into account, and the frequency domain vector quantity derived from the controller output signals and more than f previous iterations. 
     The information corresponding to the vibration frequency may be derived from a rotating shaft, where the two parts are the engine and chassis of a vehicle. 
     It is also possible generate a force between the two parts which is a harmonic of the frequency of vibration being suppressed.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to the control of vibrations. It isparticularly, but not exclusively, concerned with controlling vibrationsin an automobile, such as vibrations between the engine and itsmounting.

2. Summary of the Prior Art

EP-A-0115417 and EP-A-0172700 discussed two different types ofhydraulically damped mounting devices for damping vibration between twoparts of a piece of machinery, e.g. a car engine and a chassis.EP-A-0115417 disclosed various “cup and boss” type of mounting devices,in which a “boss”, forming one anchor part to which one of the pieces ofmachinery was connected, was itself connected via a deformable (normallyresilient) wall to the mouth of a “cup”, which was attached to the otherpiece of machinery and formed another anchor part.

The cup and the resilient wall then defined a working chamber forhydraulic fluid, which was connected to a compensation chamber by apassageway (usually elongate) which provided the damping orifice. Thecompensation chamber was separated from the working chamber by a rigidpartition, and a flexible diaphragm was in direct contact with theliquid and, together with the partition formed a gas pocket.

In EP-A-0172700 the mounting devices disclosed were of the “bush” type.In this type of mounting device, the anchor part for one part of thevibrating machinery is in the form of a hollow sleeve with the otheranchor part in the form of a rod or tube extending approximatelycentrally and coaxially of the sleeve. In EP-A-0172700 the tubularanchor part was connected to the sleeve by resilient walls, whichdefined one of the chambers in the sleeve. The chamber was connected viaa passageway to a second chamber bounded at least in part by the bellowswall which was effectively freely deformable so that it could compensatefor fluid movement through the passageway without itself significantlyresisting that fluid movement.

Both the two types of mounting devices discussed above are passive, inthe sense that they have components which are influenced by vibrations,and thus provide damping, but do not actively seek to counter thosevibrations by applying opposed vibrations. In EP-A-0262544, amodification of the “cup and boss” type mounting device was proposed, inwhich the damping characteristics of the mount were changeable independence on frequency of vibration. This provided a “semi-active”mount, but still did not provide a mounting device in which there wasactive imposition of vibrations to counter the vibrations applied to themounting device. However, it is known to apply such vibrations, toprovide an active mount in which there is cancellation of the vibrationsapplied thereto. Such mounts sense the presence of steady periodiccomponents in the vibration applied to the mount, e.g. from anautomobile engine, and by appropriate manipulation develop an opposingvariable force leading to cancellation of the vibrations, so that thevibrations are not transmitted to the supporting structure. In suchactive mounts, there must be a control relationship between thevibrations applied to the mounting device and the opposed vibrationsgenerated by the mounting device. Existing relationships depend on priorknowledge of the characteristics of the mount, which are assumed toremain fixed. It is assumed the vibration input is predominantly of asteady periodic form e.g. a sine wave (say of frequency ω) withadditional smaller random content. The aim of vibration cancellation isto input into the system an addition vibration signal which will cancelthe input (i.e. a sine wave of the same frequency and amplitude but 180°out of phase). The main problem in achieving this is that generallystructural components, through which the vibrations pass, tend to changeboth the vibration amplitude and phase. This means that what mightappear to be the correct phase of a cancellation signal at one point inthe structure may well be detrimental at another.

The steady periodic waveform being cancelled may be considered asuperposition of a number of component sinusoidal waveforms (Fouriercomponents) have differing frequencies amplitude and phase relative toeach other. Each may be characterised by its magnitude and phaserelative to some reference. Thus in the following, a particular Fouriercomponent, of a time domain signal (say x(t)) is represented as afrequency domain vector x. Similarly the characteristics of thestructure (and associated control system) through which these signalspass may be simplified by breaking it down into blocks each of which isknown to have some effect on phase and amplitude of steady periodicsignals. For example an accelerometer may convert a vibration expressedas a displacement amplitude into a voltage signal of a differingamplitude. The voltage signal from a perfect accelerometer will also be180° out of phase relative to the input. Similarly an actuator shouldproduce a force that seeks to be proportional to the displacement inputvoltage but in practice the force is likely to lag the input due to,e.g. inductance within the actuator mechanism. Quantitatively theseeffects are expressed as transfer function which give the change inphase and amplitude gain as a function of frequency. Known controlsystems have made use of iterative relationships following conversion ofthe vibrations into frequency domain phase and magnitude values.

Thus, in GB-A-2354054 use was made of vector algebra in the frequencydomain and it was proposed that an iterative relationship be used inwhich a new vector of one iteration is derived from the old vector ofthe previous iteration, plus a quantity derived from historic feedback,again in vector form. A controller is then used to generate outputsignals for the respective iterations with the output signals being infrequency domain vector form such that the output signal of oneiteration is derived from the controller output signal of theimmediately previous iteration in frequency domain vector form plus afrequency domain vector quantity derived from the resultant vibration ofmore than one previous iteration.

The system shown diagrammatically in FIG. 1 of the accompanying drawings(which will be discussed in more detail later) can be expressed usingtransfer functions (G) in a block diagram as shown in FIG. 2 of theaccompanying drawings. From this it is possible to write an expressionfor the output vibration in term of all the component effects. Each pathis summed independently and the effect of the components in each path issimply the product of all the component transfer functions.

Note that, in FIG. 2, x y are the frequency domain vectorrepresentations of a Fourier component of the input and output signal,respectively. u is an output vector signal controlling the force appliedto the mount by the control system.

In such a system, for a given unknown steady input x it is possible toexpress the relationship between y and u as follows:y=[R]•u+u ₀  (1)where [R] and u₀ are unknowns dependent on the system transfer functionsand the input x. The optimum controller output u′ leading to zero outputy can then be expressed:u′=−[R] ⁻¹ •u ₀  (2)It is possible to find a solution for u′ if two u, y data pairs exist(u_(n−1), y_(n−1), u_(n), y_(n))u′=u _(n) −[R] ⁻¹ y _(n)Where [R]⁻¹ is a matrix:

${\begin{matrix}r_{1} & {- r_{2}} \\r_{2} & r_{1}\end{matrix}}\mspace{14mu}{or}\mspace{14mu}{\begin{matrix}r_{1} & r_{2} \\{- r_{2}} & r_{1}\end{matrix}}$r ₁=(|(y _(n−1) −y _(n))|)⁻²{(y _(n−1) −y _(n))•(u _(n−1) −u _(n))}r ₂=(|(y _(n−1) −y _(n))|)⁻²{|(y _(n−1) −y _(n))x(u _(n−1) −u _(n))|}(NB “•”—dot or scalar product “x”—cross or vector product)The above is converted in an iterative control relationship thatsearches for the next best value of u′_((n+1)) based on the evidence ofthe last two attempts u′_((n)),u′_((n−1)).u′ _((n+1)) =u′ _((n)) −A[R _((n,n−1))]⁻¹ •y _((n)) +p(n)

[R_((n1 n−1))]⁻¹ is the [R]⁻¹ matrix based on the n^(th) and n−1^(th)iterations as defined above.

A is a scalar (0>A>1) defining rate of convergence and stability andp(n) is an optional small perturbation.

Hence, GB-A-2354054 proposed that the iterative control relationshipdefined above was applied to the active control of a mounting device,e.g. to one Fourier component, or any number or all of the Fouriercomponents of the vibration.

Preferably, the value of A is in the range 0.1 to 0.3 and although theperturbation p(n) may be zero, it is preferably one percent or less ofthe size of the normal control output.

When such an arrangement was used in a hydraulically damped mountingdevice, it was necessary to drive the mounting device in accordance withthe value of u. The mounting devices of EP-A-0115417 and EP-A-0172700 donot have means for applying such a driving force to the hydraulic fluid,since they are passive mounts as previously described, and thereforeGB-A-2354054 disclosed mounts in which such a drive force could beapplied.

SUMMARY OF THE INVENTION

The present invention, in its various aspects, is concerned withmodifications and developments of the active mount disclosed inGB-A-2354054. The first aspect of the present invention is concernedwith the applications of the technique of GB-A-2354054 to multiplemounts. The algorithms of GB-2354054 were concerned e.g. with where anautomobile engine is mounted on a chassis via a single mounting device,but there are two mounting devices it is necessary to ensure that theyare not driven in a way which causes their actions to conflict. If therewere two mounting devices, but the controller arrangements werecompletely separate, then it would be possible for one mount to bedriven in a way which would counteract the effect of the other mount,thereby defeating the aims of the active controller mount.

It is possible to apply the techniques discussed above to the case wherethere are two mounts, and the analysis given above may be applied.However, the terms y, u′, and [R] need to be modified.

In particular, y now represents a vector with 2*f elements where f isthe number of active mounts e.g. y=[y_(i1) y_(o1) y_(i2) y_(o2) . . . ].Each y_(i1) y_(o1) pair describes the vector (phasor) representation ofthe error signal in a similar way to that in GB-A-2354054. Similarly u′now represents a vector with 2*f elements e.g. u′=[u_(i1) u_(o1) u_(i2)u_(o2) . . . ] where each u_(i1) u_(o1) pair describes the vector(phasor) representation of the output signal as in the existing patent.[R] now represents a 2*f by 2*f matrix.

Thus, for a 2 mount system

$\quad{\begin{matrix}r_{11,1} & {- r_{11,2}} & r_{12,1} & {- r_{12,2}} \\r_{11,2} & r_{11,1} & r_{12,2} & r_{12,1} \\r_{21,1} & {- r_{21,2}} & r_{22,1} & {- r_{22,2}} \\r_{21,2} & r_{21,1} & r_{22,2} & r_{22,1}\end{matrix}}$In this case [R] has 8 unknowns which are solved at each iteration fromthe following:(y _(n) −y _(n−1))=[R](u′ _(n) −u′ _(n−1)) . . . equivalent to 4equations(y _(n−1) −y _(n−2))=[R](u′ _(n−1) −u′ _(n−2)) . . . equivalent to 4equations

where y_(n)=y at the nth iteration.

Hence, in this aspect of the invention, it is necessary to useinformation from preceding two iterations, unlike the arrangementsdiscussed in GB-A-2354054 where it was necessary to consider only onepreceding iteration. In general, there are 2*f equations which requirethe use of information from the preceding p iterations to find asolution for [R].

Thus, in the first aspect of the invention there is provided a method ofcontrolling vibrations between two parts of a structure interconnectedby f mounting devices, where f is an integer greater than 1, comprisingdamping vibrations between the two part of the structure, detecting thevibrations between the two parts of the structure, generating variableforces to oppose the vibrations transmitted by each of the f mountingdevices, and detecting any resultant vibrations due to the net effect ofsaid vibrations and said variable forces; wherein

the forces are generated under control of a controller on the basis ofan iterative relationship, the iterative relationship being such as togenerate the forces of one iteration using controller output signals infrequency domain vector form derived from the controller output signalsof f immediately previous iterations in frequency domain vector formplus a frequency domain vector quantity derived from the controlleroutput signals and the resultant vibrations of more than f previousiterations.

Moreover, this aspect of the invention also provides an apparatus forcontrolling vibrations between two parts of a structure comprising fmounting devices interconnecting the two parts of the structure, where fis an integer greater than 1, at least one detector for detecting thevibrations between the two parts of the structure and actuators forgenerating a variable forces to oppose the vibrations transmitted by therespective f mounting devices, the at least one detector being arrangedto detect the resultant vibrations due to the net effect of saidvibrations and said variable forces; wherein the actuators forgenerating the variable forces are arranged to be controlled by thecontroller to generate the forces on the basis of an iterativerelationship, the iterative relationship being such as to generate theforces of one iteration using controller output signals in frequencydomain vector form derived from the controller output signals of fimmediately previous iterations in frequency domain vector form plus afrequency domain vector quantity derived from the controller outputsignals and the resultant vibrations of more than f previous iterations.

Thus, a more complex iteration arrangement is used, but the techniquesare similar to those disclosed in GB-A-2354054.

In GB-A-2354054, it was assumed that the intention of the active controlof the mounting device was to generate vibrations within the mountingdevice which would cancel the vibrations applied to the mounting device.This would eliminate, or at least significantly reduce, transmission ofvibrations via the mounting device.

However, it has been realised that, at least for aesthetic purposes, itis sometimes desirable to apply a vibration which is not the same as thevibration input. Consider an engine vibrating in a vehicle. Thetechniques discussed above, and in GB-A2354054, it may be possible tocontrol the chassis so as substantially to eliminate the vibrations ofthe engine which are transmitted to the chassis. This eliminates thevibrations that are transmitted to the driver and passengers since thevibrations of the engine are not transmitted via the chassis to thedriver and passengers, and the chassis does not vibrate to generatesounds which would be transmitted to the driver and passenger. However,it is not always desirable wholly to eliminate such transmissive oraudio vibrations. Some help driver control, and other sounds may be seenas desirable. For example, the driver of a vehicle with a four cylinderengine may want to hear the sounds associated with a more powerful 6 or8 cylinder engine.

Therefore, a second aspect of the present invention proposes that themounting device be driven to impart a desired vibration to the two parts(such as the engine and chassis) connected by the mounting device. Thefrequency of that desired vibration is derived from one or other of thetwo parts, and/or from the vibrations therebetween, but is a harmonic ofthat frequency.

Thus, the second aspect may provide a method of controlling vibrationsbetween two parts of a structure via at least one mounting deviceconnected between the two parts of the structure, wherein:

a frequency value is derived from at least one of the two parts and/orthe vibrations therebetween;

a signal representing a harmonic of said frequency value is derived; and

the mounting device is controlled to generate a force between the twoparts such as to drive said two parts to vibrate at a frequencycorresponding to said harmonic.

This aspect may also provide an apparatus for controlling vibrationsbetween two parts of a structure via at least one mounting deviceconnected between the two parts of the structure, comprises:

a detector for detecting the vibrations between the two parts of thestructure and generating a frequency value from at least one of the twoparts and/or the vibrations therebetween;

a generator for generating a signal representing a harmonic of saidfrequency value; and

a controller for controlling the at least one mounting device togenerate a force between the two parts such as to drive said two partsto vibrate at a frequency corresponding to said harmonic.

Thus, if the two parts are an engine and a chassis, a frequency signalcorresponding to the rate of engine rotation may be derived, and themounting device controlled to generate a vibration corresponding to aharmonic of that engine frequency.

Preferably, a phase value is also derived from the at least one of thetwo parts and/or the vibrations therebetween, and the mounting device iscontrolled such that the two parts are driven to vibrate with thefrequency corresponding the harmonic and with a phase related to thephase value derived.

In this aspect it is preferable, but not essential, that the control ofthe mounting device also suppresses unwanted vibrations, in a mannersimilar to the arrangements discussed with reference to the firstaspect, or as in GB-A-2354054. In this development, the mounting devicemay be controlled to generate a variable force to oppose the vibrations,but that variable force is modified to generate the force at thefrequency corresponding to the harmonic desired. Thus, for example,vibrations at twice engine speed, which are perceived as undesirablebecause they make the engine appear unrefined, may be reduced oreliminated, and a harmonic or harmonics associated with more refinedengines imposed, e.g. at three or four times engine speed.

The third aspect of the present invention concerns the way of obtainingthe components of the vector x being a Fourier component of thevibration input from the engine, and hence obtaining vector yrepresenting the corresponding component of the output. In GB 2354054,an estimate was made of the frequency ω and x_(i,n), x_(o,n), y_(i,n)and y_(o,n) were calculated.

However, it has been realised that if the vibrations between an engineand a chassis are considered, the frequency components of the vibrationare closely related to the output rotation of the engine. The vibrationstend to be at the rate of rotation, or at harmonics or sub-harmonics ofit. Thus, rather than make use of vibration frequency ω, it is possibleto make use of a value such as a crank angle derived from the rotationof a shaft driven by the engine. That shaft may, for example, be a crankdriven directly by the engine, therefore rotating at the speed ofrotation of the engine, or some other shaft being driven at a speedrelated in a known way to the rate of engine rotation. Then, the valuethus derived can be used to replace frequency ω in the techniquesdiscussed in GB 2354054, and indeed those discussed with reference tothe first and second aspects as referred to above. However, it ispreferable that the derived value be used to replace the referencesignal x defining the engine vibration input.

Thus, in this third aspect of the present invention there may beprovided an apparatus for controlling vibrations between an engine and achassis, comprising a mounting device between the engine and thechassis, a first detector for detecting the rotation of a shaft drivenby the engine and an actuator for generating a variable force dependenton the rotation of the shaft to oppose the vibrations, a second detectorfor detecting any resultant vibration due to the net effect of saidvibrations and said variable force, and a controller for controlling theactuator for generating the variable force, wherein the actuator forgenerating the force is arranged to be controlled by the controller togenerate the force on the basis of an iterative relationship, theiterative relationship being such as to generate the force of oneiteration using a controller output signal in frequency domain vectorform derived from the controller output signal of the immediatelyprevious iteration in frequency domain vector form plus a frequencydomain vector quantity derived from the controller output signal and theresultant vibration of more than one previous iteration.

This aspect may also provide a method of controlling vibrations betweenan engine and a chassis, comprising:

detecting the rotation of a shaft driven by the engine;

damping vibrations between the two part of the structure, detecting thevibrations between the two parts of the structure, generating a variableforce dependent on the rotation of the shaft to oppose the vibrations,and detecting any resultant vibration due to the net effect of saidvibrations and said variable force; wherein;

the force is generated under control of a controller on the basis of aniterative relationship, the iterative relationship being such as togenerate the force of one iteration using a controller output signal infrequency domain vector form derived from the controller output signalof the immediately previous iteration in frequency domain vector formplus a frequency domain vector quantity derived from the controlleroutput signal and the resultant vibration of more than one previousiteration.

Moreover, this aspect may be combined with the first aspect, where thereare multiple mounting devices, by making use of the proceeding fiterations. Thus, the frequency value used in that second aspect isderived from the rotation of the shaft driven by the engine. Again, thevalue may be the frequency rotation of that shaft, or may be the valuederived from changes in crank angle which give a value equivalent to therate of rotation, and thus may be the frequency value used in the secondaspect.

Thus, this aspect may also provide an apparatus for controllingvibrations between an engine and a chassis, comprising f mountingdevices between the engine and the chassis, where f is an integergreater than 1, a first detector for detecting the rotation of a shaftdriven by the engine, actuators for generating variable forces dependenton the rotation of the shaft to oppose the vibrations in the respectivef mounting devices, at least one second detector for detecting theresultant vibrations due to the net effect of said vibrations and saidvariable force; wherein the actuators for generating said variableforces are arranged to be controlled by the controller to generate theforces on the basis of an iterative relationship, the iterativerelationship being such as to generate the forces of one iteration usingcontroller output signals in frequency domain vector form derived fromthe controller output signals of f immediately previous iterations plusa frequency domain vector form derived from the controller outputsignals and the resultant vibrations of more than f previous iterations.

It may also provide a method of controlling vibrations between an engineand a chassis interconnected by f mounting devices, where f is aninteger greater than 1, comprising damping vibrations between the twopart of the structure, detecting the vibrations between the two parts ofthe structure, generating variable forces dependent on the rotation ofthe shaft to oppose the vibrations in each of the f mounting devices anddetecting any resultant vibrations due to the net effect of saidvibrations and said variable force; wherein

the forces are generated under control of a controller on the basis ofan iterative relationship, the iterative relationship being such as togenerate the forces of one iteration using controller output signals infrequency domain vector form derived from the controller output signalsof f immediately previous iterations in frequency domain vector formplus a frequency domain vector quantity derived from the controlleroutput signals and the resultant vibrations of more than f previousiterations.

Preferably, the determination of the rotation of the shaft driven by theengine is based on a measurement of crank angle θ. The crank angle θ canthen be used to generate a sine wave which may be considered the directmeasure of input signal vector x discussed in GB-A-2354054. The resultvibration output of the chassis relative to input x may then beexpressed as:y _(i,n)=sum(y(m)• sin θ(m))/sum(θ(m)−θ(m−1))y _(o,n)=sum(y(m)• cos θ(m))/sum(θ(m)−θ(m−1))

As mentioned above, the vibrations may be at harmonics of the enginespeed, and thus the values of y_(i,n), and y_(o,n) may be generalised tothe following, where c is the harmonic number:y _(i,n)=sum(y(m)• sin(c•θ(m))/sum(c•θ(m)−c•θ(m−1))y _(o,n)=sum(y(m)• cos(c•θ(m))/sum(c•θ(m)−c•θ(m−1))

In each case, the sums are carried out by processing a block of samplesof fixed length (e.g. “k”). Preferably k is equal to the number ofsamples in a time period which is one to four times the period of thefrequency to be cancelled. As in GB-A-2354054, this may then beconverted to the time domain to give the m^(th) sample output. Theexpression for this becomes:u(m)=u _(i) sin(c•θ(m))+u _(o) cos(c•θ(m))

All of the above aspects of the present invention may make use of ahydraulically damped mounting device in which one part of the mountingdevice is driven relative to the other to impose on the mounting devicea forced vibration, in addition to its damping characteristics. Forexample, and as described in GB-A-2354054, the mounting device may havetwo anchor parts connected by a first deformable wall, a working chamberbounded by the first deformable wall and a rigid partition rigidlyassociated with a first one of the anchor parts, the working chambercontaining hydraulic fluid, a compensation chamber for the hydraulicfluid, the compensation chamber being bounded by a second deformablewall, a passageway between the chambers to allow fluid communicationtherebetween, a flexible diaphragm in direct contact with the hydraulicfluid in the working chamber, the diaphragm acting as a barrier betweenthe hydraulic fluid and a gas chamber and being fixed its periphery, andmeans for driving an intermediate part of the diaphragm to impart avibration to the hydraulic fluid, wherein the means for driving theintermediate part of the diaphragm forms said means for generating thevibrations, and the damper is formed by the interaction of the hydraulicfluid and passageway.

However the present invention is not limited to the use of such amounting device and other mounting devices may be used which provideactive driving of the components of the mounting device to impose avibrational force on the two parts connected by the mounting device, aswell as, or instead of, providing passive damping.

BRIEF DESCRIPTION OF THE DRAWINGS

Embodiments of the present invention will now be described in detail, byway of example, with reference to the accompanying drawings in which:

FIG. 1 shows the vibrating system to which the present invention may beapplied:

FIG. 2 is schematic block diagram of the system of FIG. 1;

FIG. 3 is a phase diagram of the relation between u and x;

FIG. 4 is a phase diagram of the output y;

FIGS. 5 a and 5 b show examples of the relationship between u and y;

FIG. 6 is a schematic block diagram of a controller used in the presentinvention;

FIG. 7 shows the relationship between x, y and an artificial referencer;

FIG. 8 shows in more detail a first mounting device which may be used inthe present invention;

FIG. 9 shows a second mounting device which may be used in the presentinvention;

FIG. 10 shows an embodiment of the present invention in which an engineis supported by two mounting devices;

FIG. 11 shows an embodiment of the present invention in which an engineis supported by on a chassis by four mounting devices; and

FIGS. 12 a and 12 b shows a modification of the embodiment of FIG. 10,using crank angle sensor.

DETAILED DESCRIPTION

Referring first to FIG. 1, an automobile engine 1 is mounted on achassis 2 via a mounting device 3 which, as will be described in moredetail later, provides active damping of the vibrations of the engine 1relative to the chassis 2. The engine 1 may also be connected to thechassis 2 via other mounting devices 4 which do not provide such activedamping. A feed-forward sensor 5, which may be e.g. an accelerometer,senses the input vibrations applied to the mounting device 3 from theengine 1, and a feed-back sensor 6 senses the vibrations which aretransmitted to the chassis 2 via the mounting device 3.

The mounting device 3 can be considered to have two elements, namely apassive damping element, and an actuator element operating in parallelto the passive element. A control system senses the vibrations from theengine 1 via the sensor 5, and controls the actuator of the mount 3 withthe intention of minimising the output sensed by the sensor 6. Theoutputs of the sensors 5 and 6 are thus used by the control device todetermine the signals sent to the actuator.

Note that, in the above system, it would be possible to provideadditional or alternative sensors such as a remote feed-back sensor 7,which in FIG. 1 is shown on a remote part of the chassis 2. That remotesensor could alternatively be a noise meter within the passenger cabinof the vehicle. It would also be possible for the actuator of the mount3 to be replaced by a shaker 8 which provides cancellation of thevibrations from the engine 1 under the control of the controller. It isalso possible to use a signal from an engine management system to derivea feed-forward signal either in addition to or as a replacement ofsensor 5.

The structure of FIG. 1 can be considered as a set of functions shown inthe block diagram of FIG. 2. In FIG. 2, vector x represents a Fouriercomponent of the vibration input from the engine, and vector yrepresents corresponding component of the output to the chassis 2. Thesystem can then be divided into the functional blocks shown. Note thatthe arrangement shown in FIG. 2 may be provided for more than oneFourier component of the vibration input. In FIG. 2, the functionalblock 10 represents the passive aspects of the mount 3, and thefunctional block 11 represents the effect of other vibrations paths suchas via the mount 4.

The function provided by the feed-forward sensor 5 is then shown at 12.The output y is fed back via a function 13 representing sensor 6 to thecontroller 14, which also receives the output of function 12. Thecontroller 14 then generates an output signal to be fed to the functionblock 15 representing the active aspects of the mounting device 3. Theoutputs of functions 10 and 15 are thus combined at 16 to represent thecharacteristics of the mounting device 3, and those are themselvesmodified by a function 17 presenting the structural components to whichthe mounting device 3 is attached, such as mounting brackets, etc. Theseare combined with the output from function 11, modified by function 18representing the structural effects of other vibration paths, to formthe output y.

In such a system, consider an output u sent from the controller 14 whichis some as yet unknown function of the sensed input vector x (i.e.u=G•x). u is still a vector representing a steady sine wave but it hasan amplitude and phase relative to the input signal vector x now definedby a controller transfer function. The resultant vibration output y fromthe system will be given by the followingy−sum(G_(mj)•G_(pj))x)+G_(a)•G_(pl)•G_(c)x

-   -   j=1 to q

where q is the number of vibration transfer paths

From this it can be seen that the output y will be zero if the followingholds:G _(c)=−(G _(a) •G _(pl))⁻¹•sum(G _(m j) •G _(p j))

-   -   j=1 to q        It is possible to measure the transfer functions of each        component and derive a controller which will achieve the desired        effect. These transfer functions are difficult to measure        reliably and cannot normally be transferred to other nominally        identical structures due to build variations.

The above discussion has considered vectors x, y and u being thevibration input from the engine 1, the vibration output to thesupporting structure, and control output applied by the controller 14via the mounting device 3. FIG. 3 shows an example of a controlleroutput u expressed as a vector relative to the unit magnitude input x.

By convention x is shown on the x axis and in FIG. 3 u has arbitrarily again of 1.5 and a phase of 30. In the following explanation the vectorsare also defined by their Cartesian components.

FIG. 4 shows the system response to this controller input as a vector ywhich is itself the resultant of the sum of the various vibration paths.FIGS. 5 a and 5 b then show two cases of controller output (shown on aplane defined here as the controller output plane S_(c)) and resultingsystem output (on a plane defined as the system output plane S_(s).)

The direct mapping between S_(c) and S_(s) can be expressed by therelationship used by the present invention, namely an iterative controlrelationshipu′ _((n+1)) =u′ _((n)) −A[R _((n,n−1))]⁻¹ •y _((n)),which relationship has been referred to above.

Implementation of the above relationship may be achieved with the aid ofa digital processor (i.e. a computer or a stand alone IC with DSP) whichuses sampled data via D/A and A/D converters. To devise an algorithm torepresent the relationship it is necessary to convert the time domainsignal x (t) (the sequence of samples taken every sample interval (dt))into a frequency domain representations in the form of a phase/gainvector or vectors. This is done by a method used more generally forfiltering purposes. It involves analysis of blocks of samples data asdescribed below.

One method of determining the phase and gain of y relative to the inputx is by means of an additional internal artificial reference signal rwhich is an approximation of x. r represents a sine wave with frequencyω′ which is the same or a close approximation to ω which is the truefrequency of the particular Fourier component to be cancelled. In asample case, ω′ may be the frequency derived from the rate of rotationof the engine. Since ω does not always equal ω′ there may be anadditional phase difference between x and r but this can be determinedby processing a block of samples of fixed length (e.g. “k”). Preferablyk is equal to the number of samples in a time period which is one tofour times the period of the frequency to be cancelled. Moreover, atleast for x, this is repeated at every sample. For the n^(th) iterationthe in and out of phase components (x_(i) x_(o) respectively) of xrelative to r is given by the following.x _(i,n)=sum(x(m)• sin(ω′•m•dt))/k over the range {(n−1)•k•<m≦(n)•k}x _(o,n)=sum(x(m)• cos(ω′•m•dt))/k over the range {(n−1)•k•<m≦(n)•k}Similarly for y relative to ry _(i,n)=sum(y(m)• sin(ω′•m. dt))/k over the range {(n−1)•k•<m≦(n)•k}y _(o,n)=sum(y(m)• cos(ω′•m. dt))/k over the range {(n−1)•k•<m≦(n)•k}Since x_(i), x_(o), y_(i), y_(o) are the vector components of x and yrelative to r respectively (i.e. x is a vector (x_(i), x_(o))), thevector components of y relative to x is given by the dot and vectorproducts. (see FIG. 7)y _(i,n)=(1/|x|)x•yy _(i,n)=(1/|x|)|x×y|.The above gives the n^(th) block reading of the phase and gain incartesian form of the identified Fourier component of the output y(t)relative to the input x(t). It may be calculated in block form at everyk samples to give a stepwise control function or it may be calculated asa running sum at each sample for more continuous control strategies. Inthe former it may be preferable to ignore a number of samples betweenblocks to reduce the destabilising effects of transient caused by theprevious block control signal. This process may be repeated for eachFourier component to be cancelled. In this form it can be used in theiterative algorithm described above.

The algorithm will produce the next estimate of the best control outputas a vector u′ with components u_(i), u_(o). This can be converted tothe time domain to give the m^(th) sample output from the controllerusing the following expression:u(m)=(x _(i) •u _(i) −x ₀ .u _(o))sin(ω′•m•dt)+(x _(o) •u _(i) +x _(i)•u _(o))cos(ω′•m•dt)

Since the aim of the algorithm is to produce a zero output y it followsthat with convergence, the n^(th) solution for u′ approaches that ofn−1. In these circumstances the algorithm will sleep even if ysubsequently changes. To prevent this a small perturbation iscontinuously applied to u. This perturbation is typically one thousandthof the size of the normal control output. A revised version of thealgorithm is as follows:u′ _((n+1)) =u′ _((n)) +[R _((n,n−1))]⁻¹ •y _((n)) +p(n)p_((n+1))=−p_((n))

As has previously been mentioned, it is preferable that the vector u′ isapplied to the vibrating system using a hydraulically damped mountingdevice. In accordance with the second aspect of the invention previouslymentioned, the vector u′ is applied to control the diaphragm of thehydraulically damped mounting device of the cup and boss type, which isdisclosed in EP-A-0115417.

Embodiments of such hydraulically damped mounting devices will now bedescribed in more detail.

FIG. 8 of the accompanying drawings shows one example of a “cup andboss” type of mounting device, usable with the iterative relationshipdescribed previously. The mounting device is for damping vibrationbetween two parts of a structure (not shown), and has a boss 21connected via a fixing bolt 22 to one of the parts of the structure, andthe other part of the structure is connected to a generally U-shaped cup24. A partition 27 is attached to the cup 24 adjacent a ring 26, andextends across the mouth of the cup 24 and resilient spring 25 of e.g.rubber interconnects the boss 21 and the partition 27. Thus, a workingchamber 28 is defined within the mount, bounded by the resilient spring25 and the partition 27.

The interior of the partition 27 defines a convoluted passageway 29which is connected to the working chamber 28 via an opening 30 and isalso connected via an opening (not shown) to a compensation chamber 32.Thus, when the boss 21 vibrates relative to the cup 24 (in the verticaldirection in FIG. 1), the volume of the working chamber 28 will change,and hydraulic fluid in that working chamber 28 will be forced throughthe passageway 29 into, or out of, the compensation chamber 32. Thisfluid movement causes damping. The volume of the compensation chamber 32needs to change in response to such fluid movement, and therefore thecompensation chamber 32 is bounded by a flexible wall 33.

In use, the force received by the mounting device is principallyparallel to the fixing bolt 22, and this direction defines an axis ofthe boss 21.

An annular diaphragm is then mounted on the partition 27, whichseparates the hydraulic fluid in the working chamber 28 from a gaspocket 35. If the partition 34 were able to vibrate freely, vibrationsof the boss 21 relative to cup 22 would cause forces in the hydraulicfluid in the working chamber 28 to the applied to the diaphragm 34,causing it to vibrate, and thus change the volume of the gas pocket 35.Such vibration of the partition separating the working chamber 28, fromthe gas pocket 35 would then be as described in e.g. GB-A-2282430.

However, in this mounting device, the circle defined by the mid line ofthe annular diaphragm 34 (hereinafter the centre of the diaphragm) isconnected via a connector 36 to a coil 37. The coil 37 is annular, andit intersects the magnet circuit formed by an annular permanent magnet38 and core pieces 46, 47. When a current is applied to the coil 37, itmoves axially relative to the permanent magnet 38, thus moving theconnector 38 and hence moving the centre of the diaphragm 34. Bycontrolling the current applied to the coil 37, the vibration is thencontrollable.

Preferably, the current in the coil 37 is controlled to vibrate thediaphragm 38 in harmony with the vibrations of the engines. Under thesecircumstances, the hydraulically damped mounting device may offer noresistance to the engine vibration and thus may have an effect of zerodynamic stiffness for suitable engine vibration frequency (e.g. in therange of 25 to 500 Hz). However, in addition, the diaphragm 34 separatesthe working chamber 28 from the gas pocket 35, and thus may be used totune the passive absorption of large amplitude of low frequencyvibration in a similar way to that in EP-A-0115417 or GB-A-2282430.

Thus, by combining the active vibration with the passivevibration-absorbing qualities of the diaphragm 34, an improvement may beachieved. The force applied to the diaphragm 34 from the interaction ofthe coil 37 and the, magnetic circuit formed by the magnet 38 and thecores 46, 47 apply irrespective of the current position of the diaphragm34, and thus both the active force applied to the working chamber 28 andthe passive vibration-absorbing effect may occur simultaneously. Thismay further be improved by ensuring that the engine vibrationfrequencies considered are at a frequency higher than that to which thepassageway 27 is tuned. At those frequencies, the passageway 29 iseffectively choked so that the movement of the actuator causes pressurefluctuations in the working chamber 28, rather than motion of fluidthrough the passageway 29.

In this mounting device, the drive to the diaphragm 34 is via a currentcarrying coil 37 and a permanent magnet. The permanent magnet 38 may bereplaced by an electric magnet, and it is also possible to use avariable reluctance device, particularly if a lower frequency range wasacceptable.

In the mounting device of FIG. 8, the diaphragm 34 is annular and thepassageway 30 extends through its opening. FIG. 9 illustrates anothermounting device, in which the diaphragm is circular, and is surroundedby the passageway 39. In FIG. 9, the parts of the mounting device whichcorrespond to parts of the mounting device of FIG. 8 are indicated bythe same reference numerals.

In the mounting device of FIG. 9, the diaphragm is formed by a flexiblepart 40 and a rigid part 41. They extend to close the mouth of a gaspocket 42 in a similar way to mounting devices disclosed inEP-A-0115417. The flexible part 40 of the diaphragm permits it tovibrate in response to pressure changes in the working chamber 28.

However, in addition, a coil 43 extends down from the rigid part 41 ofthe diaphragm, and is surrounded by a permanent magnet 45. Thus, byapplying a current to the coil 43, the coil 43 may be caused to vibraterelative to the permanent magnet 45, and so causing the rigid part 41 ofthe diaphragm to move. That movement of the rigid part 41 of thediaphragm is permitted due to flexing of the flexible part 40 of thediaphragm. Again, a magnetic circuit is set up since the permanentmagnet 45 is rigidly mounted on the partition 27. Thus, the embodimentsof FIGS. 8 and 9 permit a vibration to be applied to hydraulic fluid inthe working chamber 28 of a hydraulically damped mounting device,thereby to impart vibrations to that mount, and hence to the structuresto which that mount is attached. It is thus possible, to provide activecancellation of vibrations of the structures to which the hydraulicallydamped mounting device is connected.

The above discussion corresponds to the discussion in GB 2354054. Thepresent invention is concerned with developments and modifications ofthe arrangements discussed above.

In the arrangement of FIG. 1, the engine 1 is mounted on the chassis 2via a mounting device 3 which provides active damping of the vibrationsof the engine 1 relative to the chassis 2. FIGS. 10 and 11 illustrateembodiments in which there are multiple mounting devices providing suchactive damping. In the embodiments of FIGS. 10 and 11, components whichcorrespond to components of FIG. 1 are indicated by the same referencenumerals, and are not described in further detail.

In the embodiment of FIG. 10, the engine 1 is connected to the chassisvia two mounting devices 3 a, 3 b, each of which provides activedamping. The devices 3 a, 3 b may correspond to the mounting devicesshow in e.g. FIG. 8 or FIG. 9. The mounting devices 3 a, 3 b areconnected to a controller device 50, which is also connected to sensors51, 52. In such an arrangement, the controller 50 senses the vibrationsvia sensors 51, 52 and controls the mounting devices 3 a, 3 b to ensureappropriate damping.

The embodiment of FIG. 11 is similar to that of FIG. 10, but has fourmounting devices 3 a, 3 b, 3 c and 3 d. Again, those mounting devices 3a to 3 d are controlled by controller 50 on the basis of signals fromsensors 51 to 54.

The control techniques which are applied to the mounting devices 3 a and3 b in FIG. 10, and 3 a to 3 d in FIG. 11 correspond generally to thosepreviously described in reference to FIGS. 2 to 7. However, there is anextra feature that must be present. The controller 50 must co-ordinatethe controlling of each mounting device to ensure that they are notdriven in way which causes their actions to conflict. Thus, it isnecessary for the signals to each mounting device to be related, andthus the terms y, u′, and [R] are modified.

In particular, and as previously mentioned y now represents a vectorwith 2*f elements where f is the number of active mounts e.g. y=[y_(i1)y_(o1) y_(i2) y_(o2) . . . ] each y_(i1) y_(o1) pair describes thevector (phasor) representation of the error signal as in the existingpatent. Similarly u now represents a vector with 2*f elements e.g.u′=[u_(i1) u_(o1) u_(i2) u_(o2) . . . ]. Each u_(i1) u_(o1) pairdescribes the vector (phasor) representation of the output signal as inGB-A-2354054. [R] now represents a 2*f by 2*f matrix.

Hence, for the mount of FIG. 10, f=2 and y and u are vectors with fourelements.

Thus, for the 2 mount system of FIG. 10, [R] is given by the followingmatrix:

$\quad{\begin{matrix}r_{11,1} & {- r_{11,2}} & r_{12,1} & {- r_{12,2}} \\r_{11,2} & r_{11,1} & r_{12,2} & r_{12,1} \\r_{21,1} & {- r_{21,2}} & r_{22,1} & {- r_{22,2}} \\r_{21,2} & r_{21,1} & r_{22,2} & r_{22,1}\end{matrix}}$In this case [R] has 8 unknowns which are solved at each iteration fromthe following:(y _(n) −y _(n−1))=[R](u _(n) −u _(n−1)) . . . equivalent to 4 equations(y _(n−1) −y _(n−2))=[R](u _(n−1) −u _(n−2)) . . . equivalent to 4equations

where y_(n)=y at the nth iteration.

Thus, in the two mount case where f=2,u _((n+1)) =u _((n)) −A[R _(n)]⁻¹ •y _(n) +p _(n)•where:

-   u _(n)=[u_(i1), u_(o1), u_(i2), u_(o2)] is the control output signal    at the n^(th) iteration.-   y _(n)=[y_(i1), y_(o1), y_(i2), y_(o2)] is the measured vibration    signal at the n^(th) iteration.-   p=[p_(i1), p_(o1), p_(i2), p_(o2)] is an optional perturbation added    to the control output of the n^(th) iteration    -   where    -   [u_(i1), u_(o1)] forms the frequency domain vector        representation of the sinusoidal signal sent to a first mounting        device.    -   [u_(i2), u_(o2)] forms the frequency domain vector        representation of the sinusoidal signal sent to a second        mounting device.    -   [y_(i1), y_(o1)] forms the frequency domain vector        representation of the sinusoidal signal measured at a first        detection point    -   [y_(i2), y_(o2)] forms the frequency domain vector        representation of the sinusoidal signal measured at a second        detection point    -   [p_(i1), p_(o1)] forms the frequency domain vector        representation of the optional perturbation added to the control        signal sent to the first mounting device    -   [p_(i2), p_(o2)] forms the frequency domain vector        representation of the optional perturbation added to the control        signal sent to the second mounting device    -   Preferably, the signals are sinusoidal ones, and the frequency        of each sinusoidal signal is at any one of the identified        Fourier components of vibration output y(t) being cancelled. The        frequency domain vector indicates the amplitude of the signal        relative to the respective Fourier component in the vibration        input signal x(t)    -   Thus: u_(i1)=the amplitude of the sinusoidal signal sent to the        actuator of the first mount in a two mount system which is        in-phase with the respective Fourier component of the vibration        input signal x(t).    -   u_(o1)=the amplitude of the sinusoidal signal sent to the        actuator of the first mount in a two mount system which is        out-of-phase with the respective Fourier component of the        vibration input signal x(t).    -   u_(i2)=the amplitude of the sinusoidal signal sent to the        actuator of the second mount in a two mount system which is        in-phase with the respective Fourier component of the vibration        input signal x(t).    -   u_(o2)=the amplitude of the sinusoidal signal sent to the        actuator of the second mount in a two mount system which is        out-of-phase with the respective Fourier component of the        vibration input signal x(t).    -   y_(i1)=the amplitude of the sinusoidal signal measured at the        first detection point in a two mount system which is in-phase        with the respective Fourier component of the vibration input        signal x(t).    -   y_(o1)=the amplitude of the sinusoidal signal measured at the        first detection point in a two mount system which is        out-of-phase with the respective Fourier component of the        vibration input signal x(t).    -   y_(i2)=the amplitude of the sinusoidal signal measured at the        second detection point in a two mount system which is in-phase        with the respective Fourier component of the vibration input        signal x(t).    -   y_(o2)=the amplitude of the sinusoidal signal measured at the        second detection point in a two mount system which is        out-of-phase with the respective Fourier component of the        vibration input signal x(t).    -   p_(i1)=the amplitude of the optional sinusoidal perturbation        signal added to the control signal sent to the actuator of the        first mount in a two mount system which is in-phase with the        respective Fourier component of the vibration input signal x(t).    -   p_(o1)=the amplitude of the optional sinusoidal perturbation        signal added to the control signal sent to the actuator of the        first mount in a two mount system which is out-of-phase with the        respective Fourier component of the vibration input signal x(t).    -   p_(i2)=the amplitude of the optional sinusoidal perturbation        signal added to the control signal sent to the actuator of the        second mount in a two mount system which is in-phase with the        respective Fourier component of the vibration input signal x(t).    -   p_(o2)=the amplitude of the optional sinusoidal perturbation        signal added to the control signal sent to the actuator of the        second mount in a two mount system which is out-of-phase with        the respective Fourier component of the vibration input signal        x(t).        Moreover, it is preferable that A is a scalar value such that        0<A<1.-   [R_(n)]⁻¹ is the inverse of the system gain matrix [R] calculated    from u _(n), u _(n−1), u _(n−2), y _(n), y _(n−1), y _(n−2);

such that

$\begin{matrix}{\left( {{\underset{\_}{y}}_{n} - {\underset{\_}{y}}_{n - 1}} \right) = {\left\lbrack R_{n} \right\rbrack\mspace{14mu}\left( {{\underset{\_}{u}}_{n} - {\underset{\_}{u}}_{n - 1}} \right)}} & (1) \\{\left( {{\underset{\_}{y}}_{n - 1} - {\underset{\_}{y}}_{n - 2}} \right) = {{\left\lbrack R_{n} \right\rbrack\mspace{14mu}{\left( {{\underset{\_}{u}}_{n - 1} - {\underset{\_}{u}}_{n - 2}} \right)\lbrack R\rbrack}} = {\quad{\begin{matrix}r_{11,1} & {- r_{11,2}} & r_{12,1} & {- r_{12,2}} \\r_{11,2} & r_{11,1} & r_{12,2} & r_{12,1} \\r_{21,1} & {- r_{21,2}} & r_{22,1} & {- r_{22,2}} \\r_{21,2} & r_{21,1} & r_{22,2} & r_{22,1}\end{matrix}}}}} & (2)\end{matrix}$Thus the eight coefficients r_(11,1) r_(11,2) r_(12,1) r_(12,1) r_(21,1)r_(21,2) r_(22,1) r_(22,2) of [R] are solved using (1), (2) above. Ie bysolving the following eight simultaneous equationsΔy _(i1,n) =r _(11,1) *Δu _(i1,n) −r _(11,2) *Δu _(o1,n) +r _(12,1) *Δu_(i2,n) −r _(12,2) *Δu _(o2,n),Δy _(o1,n) =r _(11,2) *Δu _(i1,n) +r _(11,1) *Δu _(o1,n) +r _(12,2) *Δu_(i2,n) +r _(12,1) *Δu _(o2,n),Δy _(i2,n) =r _(21,1) *Δu _(i1,n) −r _(21,2) *Δu _(o1,n) +r _(22,1) *Δu_(i2,n) −r _(22,2) *Δu _(o2,n),Δy _(o2,n) =r _(21,2) *Δu _(i1,n) +r _(21,1) *Δu _(o1,n) +r _(22,2) *Δu_(i2,n) +r _(22,1) *Δu _(o2,n),Δy _(i1,n−1) =r _(11,1) *Δu _(i1,n−1) −r _(11,2) *Δu _(o1,n−1) +r_(12,1) *ΔΔu _(i2,n−1) −r _(12,2) *Δu _(o2,n−1),Δy _(o1,n−1) =r _(11,2) *Δu _(i1,n−1) +r _(11,1) *Δu _(o1,n−1) +r_(12,2) *Δu _(i2,n−1) +r _(12,1) *Δu _(o2,n−1),Δy _(i2,n−1) =r _(21,1) *Δu _(i1,n−1) −r _(21,2) *Δu _(o1,n−1) +r_(22,1) *Δu _(i2,n−1) −r _(22,2) *Δu _(o2,n−1),Δy _(o2,n−1) =r _(21,2) *Δu _(i1,n−1) +r _(21,1) *Δu _(o1,n−1) +r_(22,2) *Δu _(i2,n−1) +r _(22,1) *Δu _(o2,n−1),where:Δy _(i1,n)=(y _(i1,n) −y _(i1,n−1))Δy _(o1,n)=(y _(o1,n) −y _(o1,n−1))Δy _(i2,n)=(y _(i2,n) −y _(i2,n−1))Δy _(o2,n)=(y _(o2,n) −y _(o2,n−1))Δu _(i1,n)=(u _(i1,n) −u _(i1,n−1))Δu _(o1,n)=(u _(o1,n) −u _(o1,n−1))Δu _(i2,n)=(u _(i2,n) −u _(i2,n−1))Δu _(o2,n)=(u _(o2,n) −u _(o2,n−1))Δy _(i1,n−1)=(y _(i1,n−1) −y _(i1,n−2))Δy _(o1,n−1)=(y _(o1,n−1) −y _(o1,n−2))Δy _(i2,n−1)=(y _(i2,n−1) −y _(i2,n−2))Δy _(o2,n−1)=(y _(o2,n−1) −y _(o2,n−1))Δu _(i1,n−1)=(u _(i1,n−1) −u _(i1,n−2))Δu _(o1,n−1)=(u _(o1,n−1) −u _(o1,n−2))Δu _(i2,n−1)=(u _(i2,n−1) −u _(i2,n−2))Δu _(o2,n−1)=(u _(o2,n−1) −u _(o2,n−2))

For the embodiment of FIG. 11, f=4 and thus y and u have eight elementsand the matrix corresponding to [R] is an 8×8 matrix.

By linking together the iterative calculation arrangement for themounting devices this way, suitable control can be achieved.

In the arrangements discussed above with reference to FIGS. 2 to 7, anestimate was made of the frequency ω, but it is possible to make use ofa value corresponding to the rotation of the engine. Thus, and as shownin FIGS. 10 and 11, a sensor 60 may be provided which determines therate of rotation of the engine 1, and provides an input into thecontroller 50.

Such sensing of engine rotation is illustrated in more detail in FIGS.12 a and 12 b. The arrangement shown in FIGS. 12 a and 12 b correspondsgenerally to that shown in FIG. 10, and corresponding parts areindicated by the same reference numerals. However, in FIGS. 12 a and 12b, a toothed flywheel 70 is mounted on an output shaft of the engine 1and a sensor 71 is mounted adjacent the periphery of that flywheel 70,to detect the passage of the teeth. Such an arrangement, usually knownas a crank angle sensor, is already known to derive a measurement fortiming engine firing and fuel injection systems. Typically, the sensor71 is a Hall effect sensor and each pulse from the Hall sensor indicatesa fractional increment in the rotation of the flywheel 70, and hencerotation of the engine shaft on which the flywheel 70 is mounted.Intermediate rotation can then be interpolated.

Thus, if it is supposed that the toothed flywheel 70 has h teeth, theinstantaneous crank angle in degrees θ(t) is given by:

${\theta(t)} = {\left\lbrack {\frac{\left( {t - T_{N}} \right)}{\left( {T_{N} - T_{N - 1}} \right)} + N} \right\rbrack \times \frac{360}{h}}$where T_(N) is the time when the Nth tooth was sensed where N is thenumber of the tooth (from some reference point) which was sensed by thesensor 71 immediately prior to time t.

In practice, θ is sampled at multiple times, to give a series ofsamples, which will be referred to as θ(m) where m is the sample number.Thus, the equation above becomes:

${\theta(m)} = {\left( \frac{{t(m)} - T_{N}}{T_{N} - T_{N - 1}} \right) \cdot \frac{360}{h}}$where t(m) is the time of the mth sample. Then, the resulting values ofθ(m) can be used to calculate y_(i,n) and y_(o,n) as given by:y _(i,n)=sum(y(m)• sin θ(m))/sum(θ(m)−θ(m−1))y _(o,n)=sum(y(m)• cos 2(m))/sum(θ(m)−θ(m−1))

As mentioned above, the vibrations may be at harmonics of the enginespeed, and thus the values of y_(i,n), and y_(o,n) may be generalised tothe following, where c is the harmonic number:y _(i,n)=sum(y(m)• sin(c•θ(m))/sum(c•θ(m)−c•θ(m−1))y _(o,n)=sum(y(m)• cos(c•θ(m))/sum(c•θ(m)−c•θ(m−1))

In each case, the sums are carried out over successive samples (m) from1 to K, by processing a block of samples of fixed length (e.g. “k”).Preferably k is equal to the number of samples in a time period which isone to four times the period of the frequency to be cancelled.

The next output phase u′ is determined as beforeu′ _(n+1) +u′ _(n) −A[R _(n,n−1)]⁻¹ y _(n)

where u′_(n+1) has in and out of phase components u_(i) and u_(o), y_(n)comprises in and out of phase components y_(i) and y_(o) with directcrank angle measurement out signal at the (m) sample is thus formed bythe following expressionu _(n+1)(m)=u _(i) sin(c•θ(m))+u _(o) cos(c•θ(m))

So far, discussion of the development of this invention, and thediscussion of GB 2354054, has been concerned with suppressingvibrations. However, it is possible to modify those ideas to be able touse a mounting device to generate vibrations, either in addition to, orinstead of, suppressing vibrations.

At first sight, the generation of vibrations, rather than thesuppression of vibrations, may be thought undesirable. However, thereare some situations where it is desirable to generate sound, or othervibrations which could give a advantageous, rather than disadvantageous,effect.

For example, it may be desirable to generate sounds which would make theengine sound more powerful, or more refined, than it actually was.

In the simplest embodiment of this idea, it is possible to drive thecoil 37 in FIG. 8, or the coil 43 in FIG. 9 at a desired frequency andphase, to impose on the mounting device a predetermined vibration. Afrequency signal to the coil 37, 43 may be derived from a suitably tunedoscillator. The frequency and phase to which the oscillator is tuned maycorrespond to the frequency and phase of the rotation of the engine, ormay be some other frequency.

Alternatively, where the engine has a shaft angle sensor such asillustrated in FIGS. 12 a and 12 b, the signal to the coil 37, 43 may bederive directly from that sensor.

However, in this development of this embodiment, it is desirable thatnot only is a desired vibration is applied to the mount, but also thatundesirable vibrations are suppressed. This thus combines the idea ofgenerating desired vibrations with the idea of suppressing unwantedvibrations, which has previously been described.

Since this aspect proposes that the vibration is a harmonic of enginespeed, it is possible for the value of the harmonic to be derived from ashaft being driven by the engine, as in the arrangement of FIGS. 12 aand 12 b as discussed above. Thus, a value of θ may be derived in a waypreviously described, using the sensor 71, and that value then used as ameasure of the vibration. Thus, it becomes possible to make use ofharmonics of the angle measurement θ as being equivalent to harmonics offrequency ω.

It was previously mentioned that for the nth iteration,U′ _(n+1) =u′ _(n) −A[R _((n,n−1))]⁻¹ •y _(n) +p _(n)p_((n+1))=−p_((n))In that case, for a given harmonic c of angle measurement θ, the outputfrom the controller u(m) at the mth sample is given by:u(m)=u _(i) sin(cθ(m))+u _(o)• cos(cθ(m))

where c is harmonic of the frequency to be cancelled.

Then in a further equation for u(m) it is possible to add an additionalharmonic of angle measurement θ to suppress the sound of the cthharmonic but to add the sound of the dth harmonic.

u(m) is then given by:u(m)=u _(i) sin(c•θ(m))+u _(o)• cos(c•θ(m))+B _(i)• sin(d.θ(m))+B _(o)•cos(d•θ(m))

In this equation B_(i)+B_(o) represent the amplitude of the in-phase andout-of-phase components of added vibration relative to the crank anglereference at the dth harmonic.

This process may be applied to multiple harmonics to give the equation:u(m)=u _(i) ₁ sin(c _(1•)θ(m))+u _(o) ₁ cos(c ₁θ(m))+B _(i) ₁ • sin(d_(1•)(θ(m))+B _(o) ₁ cos(d ₁•θ(m))+u _(i) ₂ sin(c _(2•)θ(m))+u _(o) ₂cos(c ₂•θ(m))+B _(i) ₂ • sin(d _(2•)θ(m))+B _(o) ₂ • cos(d ₂•θ(m))+ . ..

This development of the present invention may be embodied in thestructures illustrated in FIGS. 10 and 11. As has previously beenmentioned, the sensor 60 determines the rate of rotation of the engine1. Then, the mounting devices 3 a, 3 b, 3 c or 3 d may be driven by theequation given above.

The development discussed above has assumed that this development isused to suppress unwanted vibrations, and to impose additionalvibrations at the dth harmonic. However, it is possible within thisdevelopment for there to be no suppression of unwanted vibrations. Inthis case, the mounting device is driven to vibrate at the dth harmoniconly. In such a case, u(m) is given by the following equation:u(m)=B _(i) sin(d•θ(m))+B _(o) cos(d•θ(m))

The mounting device illustrated in e.g. FIGS. 8 and 9 may be used withthis development, with signals being provided to the coils 37, 43 togenerate an appropriate vibration.

1. A method of controlling vibrations between two parts of a structureinterconnected by f active mounting devices, comprising dampingvibrations between the two parts of the structure, detecting thevibrations between the two parts of the structure, generating variableforces to oppose the vibrations transmitted by each of the f mountingdevices, and detecting any resultant vibrations due to the net effect ofsaid vibrations and said variable forces; wherein forces are generatedunder control of a controller on the basis of an iterative relationship,the iterative relationship being such as to generate the forces of oneiteration using controller output signals in frequency domain vectorform derived from the controller output signals to the f mountingdevices of f immediately previous iterations in frequency domain vectorform plus a frequency domain vector quantity derived from the controlleroutput signals to the f mounting devices and the resultant vibrations ofmore than f previous iterations; and wherein f=2 and the forces of saidone iteration are derived by use of a control relationship:u _((n+1)) =u _((n)) −A[R _(n)]⁻¹ •y _(n) +p _(n); where: u_(n)=[u_(i1),u_(o1),u_(i2),u_(o2)] is the control output signal at ann^(th) iteration; y _(n)=[y_(i1),y_(o1),y_(i2),y_(o2)] is the measuredvibration signal at the n^(th) iteration;p=[p_(i1),p_(o1),p_(i2),p_(o2)] is an optional perturbation added to thecontrol output of the n^(th) iteration; where: [u_(i1), u_(o1)] formsthe frequency domain vector representation of the sinusoidal signal sentto a first mounting device; [u_(i2), u_(o2)] forms the frequency domainvector representation of the sinusoidal signal sent to a second mountingdevice; [y_(i1), y_(o1)] forms the frequency domain vectorrepresentation of the sinusoidal signal measured at a first detectionpoint; [y_(i2), y_(o2)] forms the frequency domain vector representationof the sinusoidal signal measured at a second detection point; [p_(i1),p_(o1)] forms the frequency domain vector representation of the optionalperturbation added to the control signal sent to the first mountingdevice; [p_(i2), p_(o2)] forms the frequency domain vectorrepresentation of the optional perturbation added to the control signalsent to the second mounting device; A is a scalar value such that 0<A<1; and [R_(n)]⁻¹ is the inverse of the system gain matrix [R]calculatedfrom u _(n), u _(n−1), u _(n−2), y _(n), y _(n−1), y _(n−2); such that:$\begin{matrix}{\left( {{\underset{\_}{y}}_{n} - {\underset{\_}{y}}_{n - 1}} \right) = {\left\lbrack R_{n} \right\rbrack\mspace{14mu}\left( {{\underset{\_}{u}}_{n} - {\underset{\_}{u}}_{n - 1}} \right)}} & (1) \\{\left( {{\underset{\_}{y}}_{n - 1} - {\underset{\_}{y}}_{n - 2}} \right) = {{\left\lbrack R_{n} \right\rbrack\mspace{14mu}{\left( {{\underset{\_}{u}}_{n - 1} - {\underset{\_}{u}}_{n - 2}} \right)\lbrack R\rbrack}} = {\quad{{\begin{matrix}r_{11,1} & {- r_{11,2}} & r_{12,1} & {- r_{12,2}} \\r_{11,2} & r_{11,1} & r_{12,2} & r_{12,1} \\r_{21,1} & {- r_{21,2}} & r_{22,1} & {- r_{22,2}} \\r_{21,2} & r_{21,1} & r_{22,2} & r_{22,1}\end{matrix}}.}}}} & (2)\end{matrix}$
 2. An apparatus for controlling vibrations between twoparts of a structure comprising f active mounting devicesinterconnecting the two parts of the structure: a controller forcontrolling the f active mounting devices to control the vibrationsbetween the two parts; at least one detector for detecting thevibrations between the two parts of the structure; actuators forgenerating a variable forces to oppose the vibrations transmitted by therespective f mounting devices, the at least one detector being arrangedto detect the resultant vibrations due to the net effect of saidvibrations and said variable forces; wherein the actuators forgenerating the variable forces are arranged to be controlled by thecontroller to generate the forces on the basis of an iterativerelationship, the iterative relationship being such as to generate theforces of one iteration using controller output signals in frequencydomain vector form derived from the controller output signals to the fmounting devices off immediately previous iterations in frequency domainvector form plus a frequency domain vector quantity derived from thecontroller output signals to the f mounting devices and the resultantvibrations of more than f previous iterations; and wherein f=2 and theforces of said one iteration are derived by use of a controlrelationship:u _((n+1)) =u _((n)) −A [R _(n)]⁻¹ •y _(n) +p _(n); where: u_(n)=[u_(i1), u_(o1), U_(i2), u_(o2)] is the control output signal at ann^(th) iteration; y _(n)=[y_(i1), y_(o1), y_(i2), y_(o2)] is themeasured vibration signal at the n^(th) iteration; p=[p_(i1),p_(o1),p_(i2), p_(o2)] is an optional perturbation added to the controloutput of the n^(th) iteration; where [u_(i1), u_(o1)] forms thefrequency domain vector representation of the sinusoidal signal sent toa first mounting device; [u_(i2), u_(o2)] forms the frequency domainvector representation of the sinusoidal signal sent to a second mountingdevice; [y_(i1), y_(o1)] forms the frequency domain vectorrepresentation of the sinusoidal signal measured at a first detectionpoint; [y_(i2), y_(o2)] forms the frequency domain vector representationof the sinusoidal signal measured at a second detection point; [p_(i1),p_(o1)] forms the frequency domain vector representation of the optionalperturbation added to the control signal sent to the first mountingdevice; [p_(i2), p_(o2)] forms the frequency domain vectorrepresentation of the optional perturbation added to the control signalsent to the second mounting device; wherein A is a scalar value suchthat 0<A<1; [R_(n)]⁻¹ is the inverse of the system gain matrix[R]calculated from u _(n), u _(n−1), u _(n−2), y _(n), y _(n−1), y_(n−2); such that: $\begin{matrix}{\left( {{\underset{\_}{y}}_{n} - {\underset{\_}{y}}_{n - 1}} \right) = {\left\lbrack R_{n} \right\rbrack\mspace{14mu}\left( {{\underset{\_}{u}}_{n} - {\underset{\_}{u}}_{n - 1}} \right)}} & \; \\{\left( {{\underset{\_}{y}}_{n - 1} - {\underset{\_}{y}}_{n - 2}} \right) = {{\left\lbrack R_{n} \right\rbrack\mspace{14mu}{\left( {{\underset{\_}{u}}_{n - 1} - {\underset{\_}{u}}_{n - 2}} \right)\lbrack R\rbrack}} = {\quad{{\begin{matrix}r_{11,1} & {- r_{11,2}} & r_{12,1} & {- r_{12,2}} \\r_{11,2} & r_{11,1} & r_{12,2} & r_{12,1} \\r_{21,1} & {- r_{21,2}} & r_{22,1} & {- r_{22,2}} \\r_{21,2} & r_{21,1} & r_{22,2} & r_{22,1}\end{matrix}}.}}}} & \;\end{matrix}$
 3. An apparatus according to claim 2, wherein eachmounting device is a hydraulically damped mounting device between thetwo parts of the structure, having two anchor parts connected by a firstdeformable wall, a working chamber bounded by the first deformable walland a rigid partition rigidly associated with a first one of the anchorparts, the working chamber containing hydraulic fluid, a compensationchamber for the hydraulic fluid, the compensation chamber being boundedby a second deformable wall, a passageway between the chambers to allowfluid communication therebetween, a flexible diaphragm in direct contactwith the hydraulic fluid in the working chamber, the diaphragm acting asa barrier between the hydraulic fluid and a gas chamber and being fixedits periphery, and means for driving an intermediate part of thediaphragm to impart a vibration to the hydraulic fluid, wherein themeans for driving the intermediate part of the diaphragm forms saidmeans for generating the vibrations.